KR19980087432A - Electric press device - Google Patents

Abstract

In the transfer mechanism 4 which reciprocates the transfer arm 80 in the transfer direction of the lead frame, the movable body is centered on the first support point 31 (fixed support point) via the second support point 37 (movable support point). It is connected to the swinging cam 30 and the swinging arm 30 in pressure contact, the swinging motion of the swinging arm 30 is a linear motion of the movable body directly connected to the reciprocating motion of the transporting arm 80 In this case, the distance between the first support point 31 and the second support point 37 of the swing arm 30 is changed in the longitudinal direction of the swing arm 30 so that the transport stroke of the transfer arm 80 is changed linearly. Can be.

Description

Electric press device

The present invention relates to an electric press apparatus for performing press working to form a pilot hole in the lead frame while the lead frame is pitch-shifted to a press section having a press die.

The present invention also relates to a motor-operated press apparatus, in particular a motor-operated press apparatus capable of a press working operation by a conventional stroke and a die opening operation such as replacing a processing die.

The resin mold type semiconductor device is subjected to processing such as dambar cutting and lead molding after the resin molding process. These machining operations are performed by a press apparatus having a press die.

The press apparatus generally places the upper die and the lower die between the punch holder holding the punch and the die holder holding the die to set in the press apparatus the upper die which is hydraulically or electrically moved up and down. It is configured to perform press working while guiding by guide posts standing between the die and the lower die.

As a mechanism for transferring the lead frame from the press apparatus, the present applicant has proposed an apparatus as described in Patent Publication No. Hei 6-77376. Referring to FIG. 1, such a transfer mechanism is supported on both sides of the lead frame 101 while being pressed on the transfer plates 103a and 103b provided on the die 102. The transfer plates 103a and 103b are connected to the connecting members 104a and 104b. The transfer plates 103a and 103b may be moved up and down by a shanghai copper mechanism which will be described later. When the transfer plates 103a and 103b are pressed down, the lead frame 101 is engaged with the pilot pin 117 to be positioned on the die block 116. Reference numeral 118 denotes an erroneous detection pin that determines whether or not the lead frame is set at a predetermined position.

The transfer pins 106a and 106b are hung on the lead frame 101. The transfer pin is vertically engaged with the pilot hole 101a of the lead frame 101 from the upper side by the transfer arms 105a and 105b as shown in FIG. The transfer arms 105a and 105b are reciprocated in the lateral direction of FIG. 2 by, for example, a reciprocating mechanism reciprocated by a cylinder drive mechanism (air cylinder).

The transfer plates 103a and 103b are urged upwardly by the coil springs 107a and 107b provided on the base 107 shown in FIG. The connecting members 104a and 104b are coupled to the coupling members 109a and 109b. Lower ends of the rods 110 hanging on the coupling members 109a and 109b are connected to the swinging parts 112a and 112b fixed to the rotating shaft 111 so as to be movable upward and downward. The swinging part 112b is fixed to the rotating shaft 111. The cylinder rod of the cylinder 113 is connected to the swinging part 112b. When the cylinder 113 is operated, the rotating shaft 111 is rotated so that the transfer plates 103a and 103b pass through the swinging parts 112a and 112b, the rod 110 and the coupling members 109a and 109b. It is lowered against the pressing force of 107a.

In the press apparatus, when a conveying cylinder (not shown) is operated and the lead frame 101 is conveyed by one pitch by means of the conveying arms 105a and 105b, the cylinder 113 lowers the conveying plates 103a and 103b. The feed pins 106a and 106b are separated from the pilot hole 101 of the lead frame 101 by being operated to make it. Thereafter, the electric motor or the hydraulic mechanism is operated so that the upper die portion descends to the position where the stripper plate 115 presses the transfer plates 103a and 103b downward to perform press work. When the press working is finished, the transfer arms 105a and 105b are moved to and stay there for the die 102 while the upper die portion 114 is moved upward. The cylinder 113 is operated to move the conveying plates 103a and 103b in the upward direction, thereby supporting the pilot holes 101a of the lead frame 101 supported by the conveying plates 103a and 103b and moving upward. The transfer pins 106a and 106b are coupled. Thereafter, the transfer arms 105a and 105b are moved to transfer the lead frame 101 by one pitch to repeatedly perform the above press working.

In the above-mentioned press apparatus, three kinds of operations, namely, the vertical motion of the upper die portion by the electric motor or the pressurizing mechanism, the conveying operation of the transfer arms 105a and 105b by the cylinder drive mechanism, and the conveying by the cylinder 113 The vertical movement of the plates 103a and 103b is performed while being synchronized with each other by the electric motor. Therefore, a press cycle of one cycle requires a predetermined time (up to about 70 spm), and it is difficult to shorten the cycle time (index time).

This also applies to the press apparatus which employ | adopted the up-down motion of the upper die part by a hydraulic drive mechanism. In addition, since the number of parts is large, the manufacturing cost is high and the apparatus is also enlarged.

Since the transfer arms 105a and 105b are transferred by the cylinder drive mechanism, such transfer is performed at a constant speed. Therefore, since the impact is easily applied before and after the start and stop of the lead frame transfer operation, the lead frame is also likely to be damaged. In addition, the transfer pins 106a and 106b are also easily damaged.

The pitch of the pilot hole 101a of the lead frame 101 is changed in accordance with the type of the lead frame to adjust the feed stroke to the press section. With this adjustment, the length of the stopper bolt or the like for adjusting the movement range of the transfer arms 105a and 105b by the cylinder drive mechanism can be adjusted. In order to adjust the feed amount, it is necessary to stop the press working, so the work efficiency is reduced.

If the lead frame is set incorrectly, the operation of the press apparatus should be stopped, and the drive mechanism for the upper die portion 114 and the up / down mechanism for the transfer arms 105a and 105b and the transfer plates 103a and 103b must also be released separately. do. The lead frame is then separated from the device. Therefore, in this manner, the repair work is cumbersome.

Further, in the crank press type motor operated press apparatus, when the processing die is replaced, for example, the bottom dead center of the press ram is adjusted to obtain a predetermined processing precision. The bottom dead center of the press ram is adjusted by, for example, one of the following methods. The vertical movement shaft is screwed to the slide and rotated relative to the slide to adjust the height of the slide (Japanese Patent Laid-Open Publication No. 5-123900). The crankshaft is configured such that the eccentric position can be changed, and the adjustment is performed by adjusting the size of the eccentricity (Japanese Patent Laid-Open No. 3-216296). The adjustment is performed by changing the position of the support point of the rocker arm for pressing the ram (Japanese Patent Laid-Open Publication No. 4-157098).

In the case of a conventional press apparatus, when the processing die has to be replaced, the upper die is removed from the press ram, after which the press ram is moved up so as not to interfere with the replacement operation and the die is replaced. In the motor-operated press apparatus, the stroke range of the press ram depends on the motion range of the crank eccentric shaft. Therefore, the stroke range of the press ram must be set to a fairly large value, and in case the die is to be replaced, the replacement should be performed after moving the press ram to the uppermost position.

In the conventional motor-operated press apparatus, the range of stroke for processing is set according to the necessity of the press working operation. Therefore, the opening operation of the die during the replacement or maintenance of the die is not easily performed. In addition, the press apparatus has a configuration disadvantage in that the adjustment range is small when the bottom dead center of the press ram is to be precisely adjusted so that the adjustment is not easily performed.

In addition, other problems are caused by the use of the above-described motorized press apparatus. In other words, if a problem such as damage of the die due to misworking of the workpiece occurs during the press working, it is impossible to immediately stop the press apparatus to prevent the die from being damaged. In other words, if such a problem occurs during press processing, the press apparatus must be stopped without delay to prevent serious damage. However, it is impossible to stop the press device immediately by inertia such as a pressram. During the reset operation after jamming, the calibration during manual insertion of the operator's hand is not possible manually, which takes a long time for the reset operation.

In order to solve these problems, the present applicant has proposed a motor-operated press apparatus as described in Japanese Patent Application Laid-Open No. Hei 8-150499.

In the motor-operated press apparatus as shown in Figs. 4 and 5, the press ram 114 is connected to the crank 120 rotated by the motor to reciprocate the press ram 114 up and down. The swing link 126 is pivotally supported on a support shaft 24 which is pivotally supported on a casing installed on the top plate 110 of the press apparatus. The crank shaft 122, which is the support shaft of the crank 120, is supported on the end of the swing link 126. The drive rod 132 of the pneumatic cylinder 130 is coupled to the other end of the swing link 126 opposite to the support shaft 124.

As shown in FIG. 4, in a normal press operation, the pneumatic cylinder 130 extends the driving rod 132 upward so that the crank shaft 122, the support shaft 124, and the press ram 114 are in a straight line. Adjust the position of the swing link 126 in the arrangement. The pneumatic cylinder 130 may be pivotally supported on the casing 112 by the shaft 134 to rotate. Under this situation, one end of the oscillating link 126 is in a position further left to the vertical downward direction and abuts the stopper 36 attached to the casing 112. When the crank 120 rotates about the crank shaft 122, the press ram 114 has an upper end connected to the eccentric shaft 120a of the crank 120 and a lower end connected to the press ram 114. The press work is performed by moving up and down via the connecting rod 118. The amount of protrusion of the stopper 136 can be adjusted by using the adjustment knob 138 to adjust the bottom dead center of the press ram 114.

In an emergency during the recovery operation or the machining operation after jamming, as shown in FIG. 5, the driving rod 132 of the pneumatic cylinder 130 is retracted to rotate the swing link 126 in the counterclockwise direction. This can move the press ram 114 to the retreat position by moving the press ram 114 to the position higher than the position at the time of a normal press work.

However, the above-described motorized press device has the following problems. In a typical press working operation, the casing 112 has a high position because the crank shaft 122, the support shaft 124, and the press ram 114 are arranged in a vertical direction so as to be located in a straight line as shown in FIG. 4. As a result, the overall height of the motorized press device and the height of the press device itself increase.

When the press ram 114 is moved upward through the connecting rod 118 by rotating the swing link 126 to move the press ram 114 to the retracted position in the recovery operation after jamming or the like, the connecting The crankshaft 122 connecting the rod 118 to the swing link 126 moves vertically along an arch trajectory from a position directly below. When the press ram 114 is slightly raised, the connecting rod 114 is raised laterally as a result of the connecting rod 118 being laterally directed as shown in FIG. 5. Therefore, since a large force is required to move upward, a large pneumatic cylinder must be used as the pneumatic cylinder 130, which causes a problem in that the press apparatus must be enlarged.

If jamming or the like occurs due to the failure of the conveying operation of the workpiece during the machining operation, a large force is applied to the press ram 114. In the press working operation, as described above, the swinging link 126 is located slightly away from the vertical downward direction, and the rotation of the swinging link is regulated by the stopper 136. Therefore, no release of force occurs and this causes a problem that causes damage to the die (punch and die) and the drive mechanism.

The present invention is to solve the problems in the prior art, while reducing the index time required for the lead frame transfer operation and press operation, and at the same time to easily adjust the feed stroke when changing the varieties of the lead frame An object of the present invention is to provide an electric press apparatus which can be easily carried out, and in which the lead frame can be easily separated when the lead frame is incorrectly set.

In order to achieve the above object, the present invention provides an electric press apparatus in which press working is performed on a lead frame in which a pilot hole is formed while the lead frame is pitch-shifted to a press portion having a press die, wherein the press apparatus includes the lead frame. A transfer arm having a pin that can engage with a pilot hole of the transfer arm; a transfer mechanism for reciprocating the transfer arm in the transfer direction of the lead frame; and guiding the lead frame to be movable in the transfer direction by the press section. And a support plate installed to support and move up and down, a transport plate up and down mechanism for moving the transport plate up and down, the press unit and the feed cam arranged on the cam shaft and rotating the up and down movement cam, A drive for transmitting a drive to the transfer mechanism and the transfer plate up and down movement mechanism; And an electric motor for operating the drive transmission mechanism, wherein the moving body in the transfer mechanism is connected to the swing cam which is urged in contact with the transfer cam via a movable support point and swings about the fixed support point. The rocking motion of the arm is converted into a linear motion of the movable body which is directly connected to the reciprocating motion of the transport arm, and the distance between the fixed support point of the rocking arm and the movable support point is changed in the longitudinal direction of the rocking arm to transfer the transport stroke of the transport arm. Changes to linear.

Preferably, when the electric motor is started, the drive transmission mechanism reciprocates the press die and rotates the transfer cam and the shank cam installed on the same camshaft so that the forward or rearward movement of the transfer arm and the The lead frame is pitch-feeded by alternately guiding the upward movement or downward movement of the transfer plate.

Preferably, the transfer mechanism movably connects the movable support point to the guide groove formed in the longitudinal direction of the swing cam and reciprocates the position of the movable support point along the guide groove with the swing of the swing arm. This converts the rocking of the rocking arm into a linear motion of the moving object.

Preferably, the press apparatus further comprises a movable support point moving means capable of changing a distance from the fixed support point of the rocking cam to the linking position of the movable support point, wherein the movable support point moving means is configured to determine the linking position of the movable support point. It is driven to change along the guide groove formed in the longitudinal direction of the rocking arm.

Preferably, the support plate for supporting the toggle link mechanism is supported by a coil spring, which is applied when the transfer plate is pushed downward again by the downward motion of the upper die after the transfer plate is moved downward. Loss of absorbing pressure.

Preferably, the toggle link mechanism is configured to operate the opening and closing cylinder in an abnormal state so that the toggle link can be opened and closed.

Preferably, the support plate for supporting the toggle link mechanism is supported by a coil spring, which is applied when the transfer plate is pushed downward again by the downward motion of the upper die after the transfer plate is moved downward. Loss of absorbing pressure.

Another object of the present invention can be easily carried out by efficient stroke processing by the conventional stroke and the die opening operation in the recovery operation after jamming, and even when jamming occurs due to the reduction in the overall height of the motor-operated press apparatus. It is an object of the present invention to provide a motorized press device capable of preventing damage to the die.

In order to achieve the above object, the motor-operated press device according to the present invention,

A crank in which a support, an intermediate portion is attached to the support by a support shaft and swingable about the support shaft, and a crank shaft rotatably supported at one end of the swing link; And a press ram connected to the crank and reciprocating up and down by rotating the crank, and a driving part connected to the other end of the swing link so as to swing the swing link about the support shaft. A press device, wherein the drive unit moves the swing link upward of the press ram such that the support shaft is positioned on a first straight line extending transversely from the crank axis with respect to the movement direction of the press ram during a normal press operation. In the case of an emergency during recovery or after machining The lower end side of the swinging link lowers the press ram to move upward in the retracted position upward than in normal press operation.

As mentioned above, the swing link is in the lateral position with respect to the press ram reciprocating up and down. Therefore, the overall height of the motorized press device can be reduced compared to the case where the swing link is placed vertically on the press ram as in the prior art.

In addition, during the restoration work after jamming or the like, the swing link may be rotated such that the press ram is moved upward to a retreat position in a substantially upward direction. Therefore, the upward movement is performed more efficiently than in the prior art in which the press ram is lifted from the side.

The drive portion is connected to the first link member rotatably connected to the other end of the swing link by a first shaft, and the upper end rotatably connected to the lower end of the first link member by a second shaft. A second link member rotatably connected to the lower end by a third axis to a predetermined portion of the supporter positioned below the other end of the swing link, and the second link member rotates about the third axis; And a stopper mechanism provided on the support object and a stopper mechanism abutting the first or second link member to restrict rotation of the second link member in the direction of the press ram, wherein the rotation means is press work. In this case, the second link member is rotated in the press ram direction so that the second axis is larger than the second straight line connecting the first axis and the third axis. The first link member or the second link member is brought into contact with the stopper mechanism while being moved to the side of the ram, and in the case of the restoration work or abnormality, the second link member is rotated in the direction of the press ram facing the second link member and The other end of the swing link is lowered by moving the second shaft relative to the press ram. According to this configuration, the swing link is prevented from swinging by the repulsive force acting on the press during the press working operation.

The stopper mechanism is configured to be able to contact the first link member at a position lower than the second axis, or the second link member at a position higher than the second axis. According to this configuration, since the force applied to the stopper from the press ram via the swing link is reduced, the stopper can be miniaturized.

The stopper mechanism may be configured to receive a force greater than a predetermined force from the first or second link member abutting the stopper mechanism and to cause the second link member to rotate in the direction toward the press ram. . According to this configuration, even if jamming or the like due to the failure of the conveying work of the workpiece is applied during the press work and a large force is applied to the press ram, the stopper can absorb such a force, thereby preventing damage to the die and the press apparatus. .

In particular, the stopper mechanism includes a stopper body capable of moving along the moving direction of the second axis, pressing means for constantly pressing the stopper body in a direction in which the stopper body is separated from the press ram, and toward the second axis. And a regulating member abutting the stopper body to regulate the movement of the stopper.

In contrast, the stopper has a press in the press operation by adjusting the regulating position of the stopper body by the regulating member and adjusting the rotation amount of the first link member or the second link member in the press ram direction. An adjustment mechanism for finely adjusting the bottom dead center position of the ram may be installed.

Objects and features of the present invention other than those described above will become apparent from the following description with reference to the accompanying drawings.

1 is a plan view of a conventional press apparatus.

2 is an explanatory diagram of a transfer arm in a conventional press apparatus.

3 is an explanatory diagram showing a shape of a conventional transfer plate up and down transfer apparatus.

4 is an explanatory view showing the shapes of various parts of a conventional motorized press device in a processing state by a conventional stroke;

5 is an explanatory view showing the shapes of various parts of the conventional motorized press device in which the press ram is moved to a higher retracted position.

6 is a plan view of the drive transmission mechanism;

Fig. 7 is a side view of the drive transmission mechanism of Fig. 6 seen in the direction of arrow a.

8 is an explanatory diagram of a transfer plate vertical movement mechanism;

9 is an explanatory diagram showing the shape of main parts of the moving mechanism;

10 is an explanatory diagram showing a shape of a press section of the electric press apparatus.

11 is a front view schematically showing the shape of the electric press apparatus.

12 is a side view of the electric press device of FIG. 11 seen in the direction of an arrow b;

Fig. 13 is an explanatory view showing the shapes of various parts of the motor-operated press apparatus in the operating state by the normal stroke;

14 is an explanatory view showing states of various parts of the motor-operated press apparatus in a state where the press ram is moved to a higher retracted position.

Fig. 15 is an explanatory view seen from the side to show the operation of the press arm in the operating state by the normal stroke;

FIG. 16 is an explanatory view seen from the back of FIG. 13; FIG.

17 is an explanatory view showing a planar arrangement in a state in which the swing link is removed to show the stopper mechanism.

18 is an explanatory diagram showing a planar arrangement of a crank, a support shaft, and a first shaft attached to the swing link.

Explanation of symbols for main parts of the drawings

1,54: motor 2: press part

3: drive transmission mechanism 4: transfer mechanism

5: Shanghai Dong mechanism 7: timing belt

8: camshaft 10: press ram

13,20: Die 15: Punch Holder

16: punch 22: die holder

24: transfer plate 30: swinging arm

31: first support point 37: second support point

59: opening and closing cylinder 60: cylinder rod

68,69: toggle link 80: feed arm

80a: Pin 101a: Pilot Hole

Hereinafter, a preferred embodiment of the present invention will be described with reference to the accompanying drawings.

The embodiment will be described using an electric press apparatus equipped with a press die for a D / D (Deflash and Dambar cut system).

6 is a plan view of the drive transmission mechanism, FIG. 7 is a side view of the drive transmission mechanism as viewed in the direction of arrow A, FIG. 8 is an explanatory view of the vertical movement mechanism of the transfer plate, and FIG. It is explanatory drawing which shows a shape, FIG. 10 is explanatory drawing which shows the shape of the press part of an electric press apparatus, FIG. 11 is a front view which shows schematically the shape of an electric press apparatus, FIG. 12 is the electric press apparatus of FIG. Is the side view seen from arrow b direction.

(Overall configuration)

First, a schematic configuration of an electric press apparatus will be described with reference to FIGS. 11 and 12.

Reference numeral 1 denotes an electric motor. The press unit 2 is driven by an electric motor, and the drive is transmitted to the transfer mechanism 4 and the transfer plate up and down movement mechanism 5 described later by the drive transfer mechanism 3. The configuration of the press section 2 is shown in FIG. 10 and will not be described with reference to FIGS. 11 and 12.

In particular, the timing belt 7 is hung around the motor pulley 1a provided on the output shaft of the electric motor 1 and the first pulley 6a provided at the end of the support shaft 6 of the press section 2. The support shaft 6 is rotatably supported on a bearing portion 2a provided on the upper portion of the press portion 2. The timing belt 9 is hung around the second pulley 6a provided at the other end of the support shaft 6 and the cam shaft pulley 8a provided at the end of the cam shaft 8 of the drive transmission mechanism 3. The third pulley, not shown, is provided on the support shaft 6. The timing belt is hung around the third pulley and a pulley mounted on a crankshaft (not shown).

When the motor 1 is started, the support shaft 6 is rotated via the timing belt 7 and the crank shaft is rotated via the timing belt (not shown), whereby the crank is rotated to the crank via the connecting rod. The press ram 10 connected is moved up and down. The press ram 10 is connected to the upper die side of the press section 2.

The drive shaft 6 is rotated by the support shaft 6 via the timing belt 9 and the feed cam 11 and the shank copper 12 attached to the cam shaft 8 are rotated, thereby driving the drive. It transfers to the transfer mechanism 4 and the transfer plate Shanghai copper mechanism (5). The transfer mechanism 4 pitch-shifts the lead frame by reciprocating a transfer arm having a pin that can be engaged with a pilot hole drilled in the side rail of the lead frame. The conveying plate shank moving mechanism 5 guides the conveyance of the lead frame in the press section 2 and moves the conveying plate up and down in synchronization with the pitch conveying operation of the lead frame.

Next, each part of the electric press apparatus is demonstrated with reference to FIGS.

(Press part)

First, the structure of the press part 2 is demonstrated with reference to FIG. Reference numeral 13 denotes an upper die. An upper die driving mechanism (not shown) including the crank and the connecting rod is installed in the press casing 14 installed on the upper die 13. The lower end of the press ram 10 is connected to the punch holder 15. The press ram 10 is driven by an upper die driving mechanism to move the punch holder 15 up and down. The punch 16 is fixed by the punch holder 15. The tip of the punch 16 is guided through the stripper plate 17.

The punch holder 15 and the stripper plate 17 are connected together by an upper die support post 18. A coil string 19 is installed around the upper die support post 18 to urge the stripper 17 downward.

Reference numeral 20 denotes a lower die. The transfer plate shangdong mechanism 5 to be described later in detail is installed below the press head 21 of the lower die 20. The die holder 22 is mounted on the press head 21. The die holder 22 secures the die 23. The transfer plate 24 for guiding and supporting the lead frame so as to be moved in the delivery direction in the press section 2 is installed on the die 23 so as to be movable. The transfer plate 24 is connected to a lower die support post 25 upright on the die holder 22. A coil spring 26 is installed around the lower die support post 25 to urge the transfer plate 24 upward.

The guide post 27 is installed vertically between the punch holder 15 and the die holder 22. The guide post passes through the stripper plate 17 and the transfer plate 24 to perform positioning of the upper and lower dies 13 and 20. Upper and lower ends of the guide posts 27 are guided through the punch holders 15 and the die holders 22 by guide bushes 15a and 22a, respectively. The guide bushes 15a and 22a are fixed after the die alignment of the punch 16 and the die 23 is performed. The stripper plate 17 and the transfer plate 24 are guided to be perpendicular to the guide post 27.

(Drive transmission mechanism)

Next, the structure of the drive transmission mechanism 3 is demonstrated with reference to FIG.

As described above, the camshaft 8 is rotated by transmitting the driving force of the electric motor 1 to the pulley 8a of the camshaft. Both ends of the camshaft 8 are rotatably supported on an apparatus frame 28 which receives the drive transmission mechanism. The transfer cam 11 and the shandong cam 12 are coaxially coupled on the cam shaft 8. The transfer cam 11 transfers the drive of the cam shaft 8 to the transfer mechanism 4, and the shandong cam 12 transfers the drive of the cam shaft 8 to the transfer plate shandong mechanism 5. do. The transfer cam 11 forms a cam trajectory that performs the transfer operation at a low speed and at the beginning of the transfer operation of the lead frame by the transfer arm at low speed and during the transfer operation. The shandong cam 12 forms a cam trajectory for performing shangdong movement at a low speed at the start and stop of the up and down movement of the transfer plate 24 and at a high speed during the movement.

Reference numeral 29 in the drawing denotes a free-cam roller which is in contact with the operating surface of the transfer cam 11. The free-cam roller 29 is rotatably supported on one end of the swinging arm 30. The swinging arm 30 is supported so as to swing around the first support point 31 which serves as a fixed support point. The coil spring, not shown, is engaged with the coil spring coupling portion 30c so that the swinging arm is always pressed clockwise (see FIG. 9).

Reference numeral 32 in the drawing denotes a shandong copper cam roller which abuts against the operating surface of the vertically moving cam 12. The shandong copper cam roller 32 is rotatably supported on one end 34a of the shandong copper lever 33. The shandong copper lever 33 is pivotally rotatable about the support shaft 35 and is always pushed counterclockwise by a coil spring (not shown) so that the shandong roller 32 is the shandong cam ( It is always pressed against the operating surface of 12). The other end 34b of the shangdong lever 33 is connected at a support point 55 to one end of the link member 56 of the transfer plate shangdong mechanism 5 which will be described later.

If one end 34a of the shankdong lever 33 is swung about the support shaft 35 by the rotation of the shankdong cam 12, the link member is connected to the other end 34b at the support point 55. 56 is reciprocated laterally (see FIG. 7).

(Transportation mechanism)

The configuration of the transfer mechanism will be described below.

Referring to Fig. 9, a guide groove 30a is formed in the swinging arm 30 along the longitudinal direction of the arm. The second support point 37 serving as a movable support point is provided on the second support point plate 37 constituting a part of the movable body. The guide roller 30b is coupled into the guide groove of the swing arm 30 to connect the swing arm 30 and the second support plate 36 together. The slide member 38 is mounted on the second support plate 36. The slide member 38 is coupled to the slide rail 40 provided on the plate 39 for the vertical movement of the second support point.

When the swinging arm 30 swings, the guide roller 30b is moved into the guide groove 30a during rotation, and the slide member 38 reciprocates along the slide rail 40, thereby causing the swinging arm ( The rocking motion of 30 is converted into the linear motion of the second support plate 36.

As shown in FIG. 6, the 1st shangdong slide guide 41 is provided in a part of the 2nd support point plate 36. As shown in FIG. The 1st shangdong slide rail 41 is couple | bonded with the inside of the 1st shanghai slide rail 43 provided on the conveyance slide member 42 which comprises a part of movable body. The conveying slide member 42 is coupled to the first conveying slide rail 45 via a first conveying slide guide 44 (see FIG. 7) installed on the rear surface. The conveying slide member 42 reciprocates along the first conveying slide rail 45 while being integrated with the second support point plate 36 and is typically pulled by the coil spring 46 and the device frame 28. Stay in place on one side of the bottom (bottom of FIG. 6).

The transfer arm attachment member 47 is integrally attached to the transfer slide member 47. The transfer arm attachment member 47 is coupled to the second transfer slide rail 50 installed on the support plate 49 via the second transfer slide guide 48 (see FIG. 7) installed at the rear side.

The transfer arm attachment member 47 may be integrated with the transfer slide member 42 and reciprocate along the second transfer slide rail 50.

Referring to FIG. 6, a transfer arm attachment guide 51 is provided on the transfer arm attachment member 47. The transfer arm attachment guide 51 is attached to be opened and closed by the transfer arm attachment cylinder 52, so that the transfer arm 80 (see Fig. 7) is reliably detached.

The guide block 53 is installed on the support plate 49. The die, such as the die holder 22 of the press section 2, can be guided by a guide block to improve the attachment accuracy.

When the swinging arm 30 swings, the second support point plate 36 reciprocates along the slide rail 40 of the second support point shank-dong plate 39 as shown in FIG. The conveying slide member 42 connected to the two support plate 36 reciprocates against the pressing force of the coil spring 46 along the first conveying slide rail 45 as shown in FIG. At the same time, the transfer arm attachment member 47 connected to the transfer slide member 42 also reciprocates along the second transfer slide rail 50, and the pitch movement is performed by the transfer arm attachment member 47. The pin 80a of the transfer arm 80 attached to it is performed while maintaining the engagement with the pilot hole of the lead frame.

Referring to Fig. 9, reference numeral 54 denotes a support point moving motor for changing the distance between the first and second support points 31 and 37 of the swing arm 30 as a movable support point moving means. In particular, the ball screw 54b is attached up and down to the support point movement motor 54 via the coupling 54a. The nut 54c attached to the second support point up and down plate 39 is screwed with the ball screw 54b. When the ball screw 54b is rotated, the plate 39 for the second support point shandongdong is moved up and down via the nut 54c. The second vertical movement slide guide 39a is installed on a part of the second support point vertical movement plate 39 and is coupled to the second vertical movement slide rail 28a which is vertically formed on the apparatus frame 28. When the support point movement motor 54 rotates in a predetermined direction, the second support point vertical movement plate 39 moves up and down along the second vertical movement slide rail 28A, and passes through the slide member 38. The second support point plate 36 connected to the second support point shankdong plate 39 moves up and down along the first vertical slide rail 43 (see FIG. 6).

At this time, the slide roller 30b moves along the guide groove 30a in the longitudinal direction of the swinging arm 30. When the distance between the first and second support points 31 and 37 is shortened, for example, the size of the swing arm 30 is reduced. In proportion to the change in size, the range of the reciprocating motion of the second support point plate 30 is narrowed and the movement range of the transfer slide member 42 reciprocating integrally with the second support point plate 36 and the The range of motion of the transfer arm attachment member 47 connected to the plate is also narrowed. As a result, the conveying stroke of the conveying arm 80 is reduced. Similarly, as the distance between the first and second support points 31 and 37 becomes longer, the size of the swinging arm 30 increases. Therefore, in proportion to the increase in size, the range of the reciprocating motion of the second support point plate 36 is enlarged and the conveying stroke of the conveying arm 80 also increases.

In this manner, the swinging arm by driving the support point moving motor 54 so that the guide roller 30b provided at the second support point 37 changes the distance between the first and second support points 31 and 37. When moved along the guide groove 30a of 30, the swinging range of the swinging arm 30 can be changed. Therefore, the transfer stroke of the transfer arm 80 is changed linearly. In this embodiment, the conveying stroke of the conveying arm 80 can be arbitrarily changed within the range of about 8 to 55 by driving the support point moving motor 54.

In particular, the transfer arm 80 is switched to the linear motion of the second support point plate 36 directly connected to the reciprocating motion of the transfer arm 80 without using a plurality of links interposed with the swing arm 30. It is easy to calculate the amount of conveying strokes. Therefore, even if the items of the lead frame are changed, the adjustment of the conveying stroke can be performed very easily. Thus, the device has very good operability and processability.

Since the number of connecting parts such as rocking arm members is reduced, maintenance can be easily performed and manufacturing costs can be reduced.

(Transfer Shanghai Shanghai Organization)

Next, the structure of the transfer plate shandong copper mechanism 5 is demonstrated with reference to FIG.7 and FIG.8.

The vertical movement cam roller 32 provided at one end 34a of the vertical movement lever 33 is in pressure contact with the shank movement cam 12. When the shank lever 33 is swung about the support shaft 35 by the up and down cam 12, a link member 56 having one end connected to the support point 55 provided at the other end 34b. ) Is reciprocated laterally.

The other end of the link member 56 is connected to one end of the link member 58 at the support point 57. The other end of the link member 58 is connected to the cylinder rod 60 of the opening and closing cylinder 59. The cylinder rod 60 is in an extended or retracted state. In this embodiment, the cylinder rod 60 is in a retracted state. The opening / closing cylinder 59 is attached to two parts of the cylinder support member 59a arranged in the longitudinal direction of the member (see FIG. 11). The cylinder support member 59a is attached to the cylinder guide 63 horizontally attached to the cylinder guide attachment member 62 hanging on the base plate 61 so as to move in the lateral direction of FIG. 7. When the transfer plate 24 is moved up and down, the opening and closing cylinder 59 only serves as a link member. The support plate 49, the press bed 21, and the like are provided on the base plate 61 (see FIG. 12).

The link member 65 installed at one end of the link case 66 is connected to the cylinder case of the opening / closing cylinder 59 at the support point 64. The link member 67 is connected to the opening and closing support point 79 installed at one end of each toggle link 68,69. The other ends of the toggle links 68 and 69 are rotatably connected to the upper and lower joint plates 70 and 71, respectively. The lower joint plate 71 is a support plate for supporting the toggle mechanism. When the toggle links 68 and 69 are opened and closed, the transfer plate 24 is moved up and down with respect to the lower joint plate 71.

The lower end of the transfer plate support member 72 is connected to the upper joint plate 70. The transfer plate support member is coupled to the inside of the base plate 61 through the bearing member 73. Coupling member 74 is connected to the upper end of the transfer plate support member. The transfer plate 24 is coupled to and supported by the coupling recess 74a of the coupling member 74.

The bump member 75 is upright from the upper surface of the lower joint plate 71. When the toggle links 68 and 69 are bent and the transfer plate 24 moves downward, the upper joint plate 70 is bumped relative to the bump member to adjust the downward movement range. The spring receiving plate 76 is installed below the lower joint plate 71. The spring receiving plate 76 is attached to the spring receiving plate attachment member 76 hanging on the base plate 61. The guide post 77 is hung on the lower surface of the lower joint plate 71. The lower end of the guide post is coupled to pass through the spring receiving plate (76). Coil springs 78 are engaged around each guide post 77 to always urge the lower joint plate 71 upwards.

As shown in FIG. 11, the toggle link mechanism configured as described above is installed at the other end side of the lever 33 for vertical movement, and the left and right sides of the transfer plate 24 are respectively connected by the coupling members 74 in a vertically movable manner. Supported.

Therefore, as shown in FIG. 7, when the cam 12 for vertical movement is rotated, the shank lever 33 swings about the support shaft 35, and the opening and closing support point 79 of the toggle links 68 and 69 is rotated. ) Is reciprocated between the positions (P, Q) via a plurality of link members such as the opening and closing cylinder shown in FIG. As a result, the toggle links 68 and 69 are opened and closed, and the transfer plate 24 which engages with the coupling member 74 connected to the upper end of the transfer plate support member 72 connected to the upper joint plate 70 is up and down. Is moved to. When the cylinder rod 60 of the open / close cylinder 59 is in the extended state in the toggle links 68 and 69, the open / close support point 79 is reciprocated between the positions Q and R of FIG. .

If the lead frame is misconfigured or an incorrect detection pin (not shown) detects a failure of the lead frame setting, there is a need to stop the operation of the device, to detach the lead frame, and to recombine the pilot pin and lead frame installed on the die. . In this case, if a failure occurs during the upward movement of the transfer plate 24, the transfer plate 24 should be moved once downward. If a failure occurs during the downward movement of the transfer plate 24, the transfer plate 24 should be moved upward to support the lead frame. At this time, the opening and closing cylinder 59 of the toggle link is extended or contracted so that the cylinder rod 60 opens and closes the toggle links 68 and 69. As a result, the lead frame can be separated and the misalignment of position can be corrected. In this way, the repair of the lead frame can be performed by operating the opening and closing cylinder 59 to open and close the toggle links 68 and 69. Thus, the device has very good processability and operation.

In the press section 2, the upper die 13 is moved downward and the conveying plate 24 is moved downward against the pressing force of the coil spring provided at each end in the conveying plate width direction. At the same time, deformations such as warping may occur as a result of prolonged use (see FIG. 10). Relative measurements are made in the following manner. When the upper die 13 is moved downward, the stripper plate 17 is once moved downward until bumped against the transfer plate 24. When the transfer plate 24 is pressed further down, the lower joint plate 71 is moved downward against the pressing force of the coil spring 78. Therefore, the pressing force by the upper die 13 is absorbed by the coil spring 78. At this time, the lower end of the guide post 77 passes through the downward protrusion as the coil spring 78 is compressed. According to this configuration, the transfer plate 24 is not deformed.

(Lead frame feed operation)

The transfer operation of the lead frame of the electric press apparatus configured as described above will be described together with the press operation. In this embodiment, the conveying motion of the upper die 13, the reciprocating motion of the conveying arm 80, and the vertical motion of the conveying plate 24 are performed synchronously with each other by driving the electric motor 1. Therefore, the transfer operation while the press operation for one stroke is performed on the lead frame will be described.

First, the transfer plate 24 of the press section 2 is moved upward and the transfer pin 80a of the transfer arm 80 is engaged with the pilot hole of the lead frame on the transfer plate 24 from above. . Then, the transfer arm 80 is moved in the forward direction (arrow E direction in Fig. 6) to feed the lead frame by one pitch. Before the upper die 13 is moved downward and the stripper plate 17 presses down the transfer plate 24, the transfer plate 24 is such that the engagement of the transfer arm 80 with the lead frame becomes invalid. Is moved down. Thereafter, the transfer arm 80 returns to the initial position (in the direction of arrow F in FIG. 6) that does not correspond to the die 23 (see FIG. 10).

As the upper die 13 is further moved downward, the stripper plate 17 abuts against the transfer plate 24 to push down the transfer plate and the punch 16 causes the die 23 to press press. Enable to do so (see FIG. 10). At this time, as described above, the transfer plate 24 once reaching the range where the downward motion is possible is further pressed downward by the pressing force of the coil spring 19. However, the pressing force acting on the transfer plate 24 is absorbed by the phenomenon that the lower joint plate 71 connected to the toggle link mechanism contracts against the pressing force of the coil spring 78 (see Fig. 8).

When the press working is finished, the upper die 13 is moved upwards, the transfer plate 24 is also moved upwards, and the transfer pin 80A of the transfer arm 80 is connected to the pilot hole of the lead frame. To combine. The transfer arm 80 is then moved again in the forward direction to feed the lead frame by one pitch, and the press machining is repeated in the same way.

The index time required to perform one stroke of press working on the lead frame with the electric press apparatus was measured. As a result, the index time in the prior art was 70spm, but the index time was improved to about 200spm and high speed operation was realized.

According to this configuration, the upper die 13 is moved up and down by the drive of the electric motor 1 to perform press working, the transfer operation of the lead frame is connected together from the original through the drive transmission mechanism (3). It is performed while the transfer mechanism 4 and the transfer plate up-and-down movement mechanism 5 are synchronized with each other. Therefore, the index time required for the feed operation and the press working of the lead frame can be significantly shortened and the processing efficiency can be improved.

In particular, the transfer cam 11 and the up-and-down movement cam 12 attached to the same camshaft 8 are attached to the drive transmission mechanism 3 which drive-transmits, respectively, to the transfer mechanism 4 and the transfer plate Shanghai moving mechanism 5, respectively. The cam curves of these camshafts 11 and 12 are operated at a low speed at the start and stop of the lead frame and at a high speed during the transfer operation, whereby the feed arm can be transferred without damaging the lead frame. The breakage of the transfer pin 80a of the 80 can be reduced.

In addition, the distance between the first and second support points 31 and 37 drives the support point moving motor 54 to guide rollers installed at the second support points along the guide grooves 30a of the swinging arm 30. By moving 30b), the swing range of the swing arm 30 can be changed. Therefore, the conveying stroke of the conveying arm 80 can be changed linearly.

In particular, the transfer arm of the swing arm 30 is directly connected to the reciprocating motion of the transfer arm 80 without using the second support point 36, the transfer slide member 42, and a plurality of interposed links. Since it is converted to linear movement of the movable body such as the attachment member 47, it is easy to calculate the amount of the transfer stroke of the transfer arm 80. Therefore, even if the items of the lead frame are changed, the adjustment of the conveying stroke can be performed very easily. Thus, the apparatus has very good operability and workability.

Since the number of parts connected to the swinging arm 30 is small, maintenance can be easily performed and manufacturing cost can be low.

If the lead frame is incorrectly set, the opening and closing cylinder 59 is manually operated to open and close the toggle links 68 and 69 so that the transfer plate 24 is moved up and down. Therefore, the lead frame can be separated and position misalignment can be easily corrected, thereby improving workability and operability.

The present invention is not limited to the above embodiment. The electric press apparatus may have a plurality of punches and dies instead of a single combination of punches and dies. The press die is not limited to a press die for D / D and may be a press die for trimming and forming (T / F). It is also understood that many changes can be made without departing from the scope and spirit of the invention. For example, the press apparatus is not limited to the apparatus for punching, and the present invention can also be applied to press apparatuses which perform other kinds of press processing such as bending processing.

13 to 15 are explanatory views showing the configuration and operation of main parts of the motor-operated press device which is another embodiment of the present invention. In the figure, reference numeral 140 denotes a support of a motorized press apparatus, and reference numeral 142 denotes a casing for receiving the press apparatus. The press ram 114 is guided by a cylindrical slide guide 116 attached to the through hole 140b formed in the bottom surface 140a of the support 140 to extend downward from the bottom surface of the support 140. . The bush containing oil can be flexibly moved by the press ram 114 by being mounted on a portion of the slide guide 116 in contact with the press ram 114.

As shown in FIGS. 13 and 17, a plurality of ribs 140c are formed on the bottom surface 140a of the support 140 to which the slide guide 116 is attached to reinforce the support. According to this configuration different from the prior art, sufficient strength is ensured even if the top plate 110 is not formed thick.

The connecting rod 118 connects the press ram 114 to the crank 120. Both ends of the connecting rod 118 are pivotally supported on the shaft 114a installed on the press ram 114 and the eccentric shaft 120a of the crank 120 to press the rotary motion of the crank 120. Switch to the vertical movement of 114). The up and down stroke of the press ram 114 is adjusted by the range of rotational stroke of the eccentric shaft 120a.

The crankshaft 122 of the crank 120 is rotatably attached to one end (right end of FIG. 13) of the swing link 126 and connected to the output shaft 144a of the electric motor 144 so as to rotate.

In the prior art, ordinary electric motors (such as induction motors) such as electric motors have been used. In this embodiment, a servomotor (DC servomotor, AC servomotor, etc.) is used as the electric motor 144. By using the servo motor, the rotation of the electric motor can be stopped momentarily without providing a braking mechanism for stopping the rotation required in the prior art. Therefore, the apparatus is simplified.

When two motor-operated press devices are arranged in parallel or when a two-head press device with two press mechanisms is used, the timing of operation of each of the two press mechanisms and the workpiece feed mechanism when an electric motor such as that used in the prior art is used. Is detected by a sensor or the like, and the instruments are operated in synchronization with each other. Therefore, it is difficult to operate the entire apparatus at high speed. In contrast, the use of a servomotor allows the press mechanism to operate at a predetermined operating timing and the transfer mechanism to be operated at a predetermined operating timing in accordance with the operation of the press mechanism. Therefore, there is no need to operate the other instrument while observing the operation of one instrument, thereby improving the operating speed of the entire instrument.

The support shaft 124 is installed on the support 140 to extend horizontally. The central portion of the swing link 126 is rotatably attached to the support 140 by the support shaft 124 so that the swing link 126 can swing around the support shaft 124. Instead of the L shape used in the prior art, the swing link 126 is formed in a straight outline such that the crank shaft 122, the support shaft 124, and the first axis described later are in a straight line. The swing link is attached to extend laterally with respect to the vertical direction in which the press ram 14 is reciprocated. In the press working state shown in FIG. 13, the crank shaft 122 and the support shaft 124 are on a first substantially straight line.

Unlike the prior art example in which the oscillating link 26 is upright on the press ram 114, the oscillating link 126 in this embodiment is mounted on the oscillating link 126 so as to extend laterally or laterally. do. Therefore, the overall height of the motorized press device can be minimized.

The positional relationship between the crankshaft 122 and the press ram 114 will be described. When the oscillating link 126 oscillates around the support shaft 124, the trajectory of the crank shaft 122 draws an arc. Extending the center line of the press ram 114 is in contact with the arc.

FIG. 15 is a cross-sectional view of the swing link 126 and the crank shaft 122 seen from the front side (right side in FIG. 13).

As shown in Fig. 18, the swing link 126 is configured to integrally connect a pair of support arms 126a having a gap formed therebetween. The crank 120 is sandwiched between a pair of support arms 126a. A crank shaft 122 protruding from the side of the crank 120 is rotatably supported on the support arm 126a. The eccentric shaft 120a formed at the center of the crank 120 rotatably penetrates the upper end of the connecting rod 118, and the press ram 114 is rotatably attached to the lower end by the shaft 114a. do.

A first pulley 146 for transmitting torque to the crank 120 is installed on the outer side of one support arm 126a of the swing link 126 and connected to the crank shaft 122.

The outline of the drive system for moving the press ram 114 up and down will now be described. As shown in FIG. 18, the second pulleys 148a and 148b are respectively connected to both ends of the support shaft 124 arranged horizontally on the support 140. The electric motor 144 is installed on the side opposite to the crank 120 side with respect to the support shaft 124. The third pulley 150 is connected to the outer shaft 144a of the motor. The belts 152a and 152b are hung around the first pulley 146 and the second pulley 148b, the second pulley 148b and the third pulley 150, respectively, so that the driving force of the electric motor 144 is zero. 1 is transmitted to the pulley 146 to rotate the crank 120. Rotation of the crank 120 causes the press ram 114 to move up and down.

The drive unit 154 is connected to the front end of the other end side (left end) of the swinging link 126 which lies almost horizontally in FIG. The driving unit 154 swings the swing link 126 about the support shaft 124 to move the press ram 114 up and down.

The drive unit 154 swings so that the support shaft 124 is positioned on a first straight line A extending laterally from the crank shaft 122 with respect to the moving direction of the press ram 114 in a normal press working operation. A function of adjusting the position of the link 126 and lowering the other end of the rocking link 126 to rotate the rocking link 126 in a counterclockwise direction during jamming during a machining operation or a reset operation after an emergency is performed. It has a function of positioning the press ram 114 upwards to a retracted position above the position where the ram performs a normal press working operation.

The configuration of the drive unit 154 will be described in detail.

In the same manner as the prior art, the drive unit 154 may be composed of a pneumatic cylinder 130, the drive rod 132 of the pneumatic cylinder is the other end of the swing link 126 to swing the swing link 126 Can be connected directly to In this embodiment, instead of the configuration in which the oscillating link 126 is directly oscillated by the pneumatic cylinder 130, a configuration in which the oscillating link 26 oscillates through two links as shown in FIG. 13 may be employed. Can be.

In particular, the driving unit 154 is the first link member 158 and the first link member 158 which is rotatably connected to the upper end by the first shaft 156 on the other end side of the swing link 126, the first link member 158 The lower end of the support shaft 140 is rotatably connected to the lower end of the support shaft 140 by the second shaft 160 and positioned below the other end of the swing link. A second link member 164 rotatably connected, and rotation means for rotating the second link member 164 about the third shaft 162 (for example, the pneumatic cylinder 130). It includes.

The stopper is installed on the support 140 and is in contact with the first or second link member 164 to restrict the rotation of the second link member 164 toward the press ram 114. Further includes an instrument 166. In this embodiment, for example, the stopper mechanism 166 abuts on the lower end of the first link member 158. Alternatively, the stopper mechanism 166 may abut on an upper end of the second link member 164.

As shown in FIG. 17, one end of the pneumatic cylinder 130 is rotatably attached to the support 140 by a shaft 134. The tip end of the driving rod 132 is rotatably connected to the second shaft 160.

In the press working operation, the driving rod 132 of the pneumatic cylinder 130 has a second straight line connecting the first and third lines 156 and 162 by rotating the second link member 164 toward the press ram 114. It is retracted to move the second shaft 160 toward the press ram 114 beyond B). In this case, the lower end portion of the first link member 158 contacts the stopper mechanism 166 to restrict the rotation of the second link member 164. Thereafter, the pneumatic cylinder 130 maintains a state of pressing the second link member 164 in the same direction. At the same time, the first and second link members 158, 164 are bent in an L shape directed towards the press ram 114 as shown in FIGS. 13 and 16. If a repulsive force acting on the press ram 114 during the press working operation is applied to the first and second link members 158 and 164 via the swing link 126, the direction of action of the force is the second link member 164. The first link member 158 reliably receives the kinetic force in the direction in which the member abuts against the stopper mechanism 166 since the first link member 158 always coincides with the direction of rotation toward the press ram 114. Thus, the swing link 126 is reliably prevented from rotating in the counterclockwise direction.

As described above, the stopper mechanism 166 reliably holds the swing link 126 in a lateral state during the press working operation and the first link member 158 for adjusting the bottom dead center of the press ram 114. By changing the contact position with respect to the ()) it has a function of slightly changing the regulation position of the swing link 126 determined by the stopper mechanism 166.

In this embodiment, the stopper mechanism 166 of the second link member 166 toward the press ram when the force applied from the abutting first and second link members 158, 164 exceeds a predetermined position (estimated value). It has another function that enables rotation.

Due to this function, even if jamming or the like occurs due to the failure of the workpiece conveyance operation and a force larger than a predetermined value is applied to the press ram 114, the rotation of the second link member, which has been restricted in rotation, is further restricted and the force This can be absorbed. Therefore, the die and the press device are prevented from being damaged.

The configuration of the stopper mechanism 166 will now be described with reference to FIGS. 16 and 17.

The stopper body 68 directly abuts the first link member 158 (or second link member 164). For example, when the stopper body 168 protrudes into a rod shape, one end (lower end in FIG. 17) is pivotally supported on the wall of the support by the shaft 168a so that the stopper body can rotate in a horizontal plane. To be able. The contact portion 168b which is in contact with one side surface of the first and second link members 158 and 164 is provided on the side surface of the first link member 158 (or the second link member 164). When the stopper body 168 is rotated, the abutting portion 168b provided on the side surface is moved in an arc shape along the moving direction of the second shaft 160 (direction of arrow C in FIG. 17).

The restricting member 170 abuts against the stopper body 168 to regulate the movement of the stopper body 168 toward the second shaft 160. For example, the restricting member is formed in a rod shape, one end (left end of FIG. 16, right end of FIG. 17) is screwed to the support 140, and the other end (right of FIG. 16, FIG. 17). Left) is attached to the support 140 to pass through the rotatable end of the stopper body 168. The restricting member 170 is installed to extend in the longitudinal direction of the swing link 126. The first large diameter portion 170a is formed at the other end of the restricting member 170 penetrating the stopper body 168 to protrude. The second large diameter portion 170b is formed at a position separated from the first large diameter portion 170a so as to cross the stopper body. Therefore, the free end of the stopper body 168 may move between the first and second large diameter portions 170a and 170b.

The coil spring 172 is removably attached between the free end of the stopper body 168 and the second large diameter portion 170b in such a manner that the coil spring is coupled onto the restricting member 170. The coil spring functions as a pressing member that always presses the stopper body 168 in the direction in which the stopper body 168 is separated from the press ram 114 with respect to the second large diameter portion 170b. The pressing force of the coil spring 172 may be arbitrarily set according to the diameter and material of the wire member and the clamping force applied to the inserting portion. Instead of the coil spring 172, a spiral spring, a flat spring and the like can be used.

Since one end of the regulating member 170 is screwed to the support 140, the position of the first large diameter portion 170 in the longitudinal direction of the regulating member may be changed by rotating the regulating member 170. Therefore, the position of the stopper body 168 which is always pushed by the coil spring 172 to abut on the first large diameter portion 170a can be changed, so that the stopper body 168 determined by the stopper mechanism 166. The regulatory position of can also be changed. Therefore, the bottom dead center of the press ram 114 can also be adjusted.

In the stopper mechanism 166 of the embodiment, the coil spring 172 is applied when a force exceeding the pressing force of the coil spring 172 is applied from the first or second link members 158 and 164 in contact with the stopper body 168. The second link member 164 is retracted to be able to rotate towards the press ram 114. In consideration of the strength of the die driven by the press ram 114 and the strength of the swing link 126, the first and second link members 158, 64, etc. constituting the motorized press device, the coil spring 172 ) May be preset to a predetermined value. As a result, even if jamming or the like due to the failure of the workpiece conveyance operation occurs during the machining operation and a force greater than the predetermined value is applied to the press ram 114, the second link member 164 whose rotation is restricted is held by the force. By further rotating to absorb the die, the die and the press apparatus are protected from damage.

Reference numeral 174 in the drawing indicates an adjustment knob attached to one end of the restricting member 170. The restricting member 170 is reciprocated in the longitudinal direction by manually rotating the adjusting knob 174. Rotation of the regulating member 170 may be performed by an electric motor or the like instead of manual operation. A load cell may be installed in the press ram 114 to detect the pressure applied to the press ram 114, and the electric motor is driven in accordance with the detected pressure to automatically adjust the bottom dead center of the press ram 114. Can be performed.

In this embodiment, the lower end portion of the first link member 158 extends downwardly beyond the second shaft 160, and the stopper mechanism 166 is disposed below the second shaft of the first link member 158. It is comprised so that a part of 1 link member 158 may contact. Therefore, according to the principle of the lever, the rotation of the link member 164 is less than the force when the stopper mechanism 166 is in direct contact with the vicinity of the second shaft 160 to prevent the swing link 126 from rotating. Can be regulated by force. Thus, the coil spring 172 can be downsized in size and the stopper and consequently the entire press device can be downsized. Instead of this configuration, the upper end of the second link member 164 may extend upwardly beyond the second axis 160, the stopper mechanism 166 being a second link above the second axis 160. A portion of the member 164 may be in contact.

13 and 16 (shown in the opposite direction to the direction of FIG. 13) show a state in which the swing link 126 is in the lower position and a conventional press working operation is performed by a conventional press ram 114. . 15 illustrates a method of moving the press ram 114 up and down. In particular, the portion on the left side with respect to the center line shows the state in which the press ram 114 is lowered, and the portion on the right side shows the state in which the press ram 114 is raised. The press ram 114 is moved up and down by rotating the crank 120 via the drive system by the motor 144.

Fig. 14 shows another state of use of the motorized press device, or the state in which the press ram 114 is further moved above the stroke range in normal operation. The movement of the press ram 114 to the upper position is as follows. In the same case, the press ram 114 is moved to a position which does not interfere with the work in case of a problem in a normal work, when the press working operation must be stopped immediately, and in the recovery work after jamming. This is the case.

If a problem such as damage of the die due to misworking of the workpiece occurs during the press working, for example, the apparatus of the present embodiment can operate in the following manner. That is, the pneumatic cylinder 130 is immediately activated to rotate the oscillating link 126 in the counterclockwise direction, the press ram 114 is raised to a position higher than the position where the press ram is located in a typical press operation. Direction so that the press ram 114 can be moved to the retracted position. The press ram 114 has a constant level of inertia. If the press ram is forcibly moved away from the working position as in the case of the present embodiment, the press ram can be retracted momentarily in a manner appropriate for the inertia.

The apparatus as in the above embodiment in which the press ram 114 is moved upwards to a position higher than a normal machining position has an advantage that an operation such as a recovery operation after jamming can be easily performed. In the apparatus of this embodiment, the setting of the press ram in particular to a high retracted position can be easily performed by the rotational operation of the swing link 126 by the pneumatic cylinder 130. The movement of the press ram 114 can be performed immediately. Therefore, the device is easy to operate. In addition, the device is characterized in that after operation, the press ram 114 can be easily and quickly set to a position in a normal working state.

When the press ram 114 is moved above the position of the normal working state, the driving rod 132 of the pneumatic cylinder 130 is projected (to the position indicated by the broken line in Fig. 16), the second link member ( 164 is rotated in a direction opposite to the press ram 114, and the second shaft 160 is moved beyond the second straight line B to the opposite side of the press ram 114. In this case, when the second link member 164 is rotated to a predetermined angle or more, one end of the swing link 126 is lowered through the first link member 158, and thus the swing link 126 The other end of is also moved upward. This moves the press ram upwards to the retracted position higher than the position to be placed in normal press working.

As described above, extending the centerline of the press ram 114 in this embodiment contacts the circular arc in which the crank shaft 122 is moved when the swing link 126 swings about the support shaft 124. Therefore, in the reset operation or the like, the fraud press ram 114 is raised almost vertically by rotating the swing link 126 to move to the retracted position. The resistance between the press ram and the slide guide 116 is lower than in the prior art configuration in which the press ram 114 is raised from the side, so the upward motion can be performed efficiently. As a result, the pneumatic cylinder 130 of the drive unit 154 is smaller than that of the conventional embodiment, so that the press apparatus can be miniaturized.

The rotation of the oscillating link 126 may be performed after the rotation of the crank is stopped in the press working operation. Alternatively, the swing link 126 may be performed without stopping the rotation of the crank.

As described above, according to the present invention, the upper die is moved up and down by an electric motor to perform a press operation, and the transfer operation of the lead frame is performed by the transfer operation of the lead frame and the shank movement of the transfer plate. This is done while synchronizing with each other. Therefore, the index time required for the lead frame transfer operation and the press working operation can be significantly shortened and the work efficiency can be improved.

In particular, the drive transmission mechanism for driving transmission to the transfer mechanism and the transfer plate shangdong moving mechanism, respectively, is provided with a transfer cam attached to the same cam shaft and the vertical movement cam, and the cam curves of these cam shafts when starting and stopping the feed of the lead frame At a low speed, by operating at a high speed during the transfer operation, it is possible to transfer without damaging the lead frame and to reduce the breakage of the transfer pin of the transfer arm.

Further, the distance between the rocking center line of the rocking arm and the rocked position of the movable body can linearly change the transport stroke of the transport arm by driving the movable support point moving means to change the rocking arm in the longitudinal direction.

In particular, it is easy to calculate the amount of transfer stroke of the transfer arm since the swing arm is converted to linear movement of the movable body directly connected to the reciprocating movement of the transfer arm without using a plurality of links interposed therebetween. Therefore, even if the items of the lead frame are changed, the adjustment of the conveying stroke can be performed very easily. Thus, the apparatus has very good operability and workability.

Since the number of parts connected with the swinging arm is small, maintenance can be easily performed and manufacturing cost can be low.

If the lead frame is incorrectly set, the opening and closing cylinder is manually operated to open and close the toggle link mechanism so that the transfer plate is moved up and down. Therefore, the lead frame can be separated and position misalignment can be easily corrected, thereby improving workability and operability.

According to the motor-operated press apparatus of the present invention, the die opening operation in the efficient press working operation by the ordinary stroke and the recovery work after jamming can be easily performed, and the side position with respect to the press ram reciprocating up and down By means of the arrangement of the oscillating link, the overall height of the motorized press device is reduced compared to the prior art configuration in which the oscillating link is installed above and below the press ram.

Further, in the recovery operation after jamming, the press ram can be raised almost in the vertical direction by rotating the swing link to move to the retracted position. Therefore, the upward motion can be performed more efficiently than the prior art configuration in which the press ram is raised from the side. As a result, the driving portion can be made smaller and the whole press apparatus can be made smaller.

When the stopper mechanism receives a force greater than a predetermined value from the first or second link member, the stopper mechanism causes the second link member to rotate in the direction of the press ram. Therefore, the present invention can prevent the die and the press apparatus from being damaged by absorbing the force even if jamming or the like due to the failure of the workpiece transfer operation occurs during the press operation and a large force is applied to the press ram.

The foregoing description of the preferred embodiments of the present invention has been presented for purposes of illustration and description, and is not limited to the same forms as described. Modifications and variations of the present invention may be made in light of the above description and may be achieved from practice of the present invention. The above embodiments are selected and described to illustrate the principles of the invention and those skilled in the art can use the principles of the invention in a number of embodiments with various modifications. It is to be understood that the scope of the invention is only limited by the appended claims and equivalents thereof.

Claims (13)

An electric press apparatus for performing press working to form a pilot hole in the lead frame while the lead frame is pitch-shifted to a press section having a press die, comprising: a transfer arm having pins engageable with pilot holes of the lead frame; A conveying mechanism for reciprocating the conveying arm in the conveying direction of the lead frame, and a conveying portion provided at the press section to guide and support the lead frame so as to be movable in the conveying direction and to be movable up and down A plate, a conveying plate vertical movement mechanism for moving the conveying plate up and down, and a driving cam and a conveying cam arranged on a cam shaft, and a conveying cam arranged on a cam shaft to rotate the conveying mechanism and the conveying plate vertical movement mechanism. A drive transmission mechanism for transmitting drive to the furnace, and an electric drive for operating the drive transmission mechanism. And a moving body is connected to the swinging cam which is urged in contact with the transporting cam and is pivoted about a fixed support point via a movable support point, wherein the rocking motion of the rocking arm is a reciprocating motion of the transporting arm. The moving press is converted into a linear motion of the moving body directly connected to, the distance between the fixed support point and the movable support point of the swinging arm is changed in the longitudinal direction of the swinging arm to change the transfer stroke of the transfer arm linearly Device. 2. The forward or rearward movement of the transfer arm as set forth in claim 1, wherein the drive transmission mechanism reciprocates the press die and rotates the transfer cam and the shank east cam installed on the same camshaft when the electric motor starts. An electric press apparatus for pitch-feeding the lead frame by alternately guiding movement and upward movement or downward movement of the transfer plate. 2. The transfer mechanism according to claim 1, wherein the transfer mechanism movably links the movable support point to the guide groove formed in the longitudinal direction of the swing cam, and reciprocates the position of the movable support point along the guide groove along with the swing of the swing arm. And a rocking motion of the rocking arm to convert the rocking arm into a linear motion of the movable body. 4. The electric press apparatus according to claim 3, wherein the electric press apparatus further comprises movable support point moving means capable of changing a distance from the fixed support point of the swing cam to the linking position of the movable support point, wherein the movable support point moving means And a linking position driven along the guide groove formed in the longitudinal direction of the swinging arm. 2. The electric press apparatus as set forth in claim 1, wherein the transfer plate vertical movement mechanism moves the transfer plate vertically through a toggle link mechanism which is opened and closed in association with the vertical movement lever which rotates in pressure contact with the vertical movement cam. . 6. The electric press apparatus according to claim 5, wherein the toggle link mechanism is configured to operate the opening and closing cylinder in an abnormal state so that the toggle link can be opened and closed. 7. The support plate according to claim 6, wherein the support plate for supporting the toggle link mechanism is supported by a coil spring, and the coil spring presses the transfer plate downward again by downward movement of the upper die after the transfer plate is moved downward. The electric press apparatus which absorbs the pressing force applied in the case. A crank in which a support, an intermediate portion is attached to the support by a support shaft and swingable about the support shaft, and a crank shaft rotatably supported at one end of the swing link; And a press ram connected to the crank and reciprocating up and down by rotating the crank, and a driving part connected to the other end of the swing link so as to swing the swing link about the support shaft. In the press type press, the drive unit is adapted to move the swing link of the press ram such that the support shaft is positioned on a first straight line extending transversely from the crank axis with respect to the movement direction of the press ram during normal press operation. Adjust to the side position in the upward direction and recover after jamming or during When the motor-operated press machine, comprising a step of moving upward the press ram is lowered to the other end of the swing link to a normal retracted position upper than that during the press working. The upper end portion of claim 8, wherein the driving portion comprises: a first link member rotatably connected to the other end of the rocking link by a first shaft, and an upper end portion of the lower end of the first link member by a second shaft; A second link member rotatably connected to the supporter, the lower end being rotatably connected by a third shaft to a predetermined portion of the supporter positioned below the other end of the swing link, and the second link member being connected to the second link member. Rotating means for rotating about a third axis, and a stopper mechanism mounted to the support object and abutting against the first or second link member to restrict rotation of the second link member toward the press ram; And the rotating means rotates the second link member in the press ram direction during the press work so that the second shaft connects the first shaft and the third shaft. The first link member or the second link member is brought into contact with the stopper mechanism while being moved toward the press ram side from the line, and in case of the restoration work or abnormality, the second link member is rotated in the opposite press ram direction and 2. The motor-operated press apparatus as claimed in claim 2, wherein the other end of the swing link is lowered by moving the second shaft opposite to the press ram with respect to the straight line. 10. The motor operated type according to claim 9, wherein the stopper mechanism abuts on the side of the first link member at a position lower than the second axis, or on the side of the second link member at a position higher than the second axis. Press device. 10. The stopper mechanism according to claim 9, wherein the stopper mechanism receives the force greater than a predetermined value of the first or second link member in contact with the stopper. Motor-operated press apparatus, characterized in that the rotatable. The method of claim 9, wherein the stopper is a stopper body capable of moving along the moving direction of the second axis, pressing means for always pressing the stopper body in a direction in which the stopper body is separated from the press ram, and the second And a restricting member abutting on the stopper body to regulate the movement of the stopper toward an axis. 13. The stopper as set forth in claim 12, wherein the stopper includes a regulating position of the stopper body by the regulating member and adjusting the rotational amount of the first link member or the second link member in the press ram direction. And an adjustment mechanism for finely adjusting the bottom dead center position of the press ram.